JP2003343440A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of reducing oil outflow quantity from a gas extracting passage in simple constitution. <P>SOLUTION: The gas extracting passage 31 to constantly communicate a crank chamber 5 with an intake chamber is provided in a drive shaft 10, and an inlet part 36 of the gas extracting passage 31 facing the crank chamber 5 is set in a diametric direction of the drive shaft 10. Mist oil flowing into the gas extracting passage 31 with blow-by gas first collides with an inner circumferential surface of the inlet part 36 of the gas extracting passage 31 by rotary motion of the drive shaft 10. Oil is thus separated (gas-liquid separation) at the inlet part 36 of the gas extracting passage 31. Next, oil separated from the blow-by gas at the inlet part 36 of the gas extracting passage 31 is pushed to return to the crank chamber 5 as it is by centrifugal force by rotary motion of the drive shaft 10. It is therefore hard to flow out with flow of the blow-by gas into the intake chamber. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor which is installed in a refrigerating cycle such as a vehicle air conditioner and used for compressing a refrigerant gas.

[0002]

2. Description of the Related Art In compressors, lubricating oil is stored in the crank chamber in order to supply the lubricating oil to the sliding parts in the crank chamber. Since the compressor has a bleed passage that connects the crank chamber and the suction chamber, there is a problem that lubricating oil flows from the crank chamber to the suction chamber through the bleed passage.

That is, when the lubricating oil is taken out from the crank chamber, the following two problems mainly arise. First, if lubricating oil is taken out of the crank chamber and the oil supply to the sliding components in the crank chamber is insufficient, the sliding components are adversely affected. Secondly, the lubricating oil flows from the crank chamber to the crank chamber → suction chamber → cylinder bore → discharge chamber → outside the compressor → refrigerating cycle heat exchanger (condenser,
When it flows into the evaporator, the lubricating oil adheres to the thin tubes of the heat exchanger and reduces the heat exchange efficiency.

[0004]

[Patent Document 1] Japanese Patent Laid-Open No. 62-203980

[0005]

From this point of view,
As disclosed in Japanese Patent Laid-Open No. 58-158382, a conventional compressor has a structure in which a control valve is connected to the outlet of the extraction passage and the control valve is expected to have the same function as an orifice. However, in this conventional control valve, the opening / closing valve of the extraction passage is closed when the compressor is stopped, and the opening / closing valve of the extraction passage is opened when the compressor is activated. Therefore, even if the oil is separated, the oil gradually flows out along with the gas flow. Moreover, the ventilation passage through the control valve becomes complicated.

The present invention has been made based on such a conventional technique, and an object thereof is to provide a compressor capable of reducing the oil outflow amount from the extraction passage with a simple structure.

[0007]

According to a first aspect of the present invention, a front housing is joined to a front end surface of a cylinder block having a cylinder bore for accommodating a piston to form a crank chamber, and the cylinder block is provided. In the compressor, the rear housing is joined to the rear end surface to form a suction chamber and a discharge chamber, and the piston reciprocates by utilizing the rotation of the drive shaft axially supported in the crank chamber,
A bleed passage that constantly connects the crank chamber and the suction chamber is provided in the drive shaft, and an inlet portion of the bleed passage is set in the radial direction of the drive shaft and directly faces the crank chamber. It is a feature.

[0008]

According to the first aspect of the present invention, the bleed passage which constantly connects the crank chamber and the suction chamber is provided in the drive shaft, and the inlet portion of the bleed passage is set in the radial direction of the drive shaft. Since it is characterized by directly facing the room,
The mist-like oil, which tends to flow into the extraction passage together with the blow-by gas, first collides with the inner peripheral surface of the inlet portion of the extraction passage by the rotational movement of the drive shaft and is captured. That is, oil is separated (gas-liquid separation) at the inlet of the extraction passage. Next, the oil separated from the gas at the inlet of the bleed passage is pushed back into the crank chamber by the centrifugal force due to the rotational movement of the drive shaft, so that the structure is less likely to flow into the suction chamber. That is, according to the first aspect of the invention, the bleed passage is a passage that always connects the crank chamber and the suction chamber without passing through the control valve, but has a structure that actively separates oil (gas-liquid separation). The oil outflow amount from the extraction passage can be reduced with a simple structure.

[0009]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

First Embodiment: FIGS. 1 to 3 show a first embodiment of the present invention. As shown in FIG. 1, the compressor 1 of this embodiment is a swash plate type variable displacement compressor. The swash plate type variable displacement compressor 1 includes a cylinder block 2 having a plurality of cylinder bores 3, a front housing 4 joined to a front end surface of the cylinder block 2 to form a crank chamber 5 between the cylinder block 2 and the front housing 4. A rear housing 6 joined to the rear end surface of the cylinder block 2 via a valve plate 9 to form a suction chamber 7 and a discharge chamber 8 is provided. The cylinder block 2, the front housing 4, and the rear housing 6 are fastened and fixed by a plurality of through bolts B through a plurality of through bolt through holes (not shown) provided in the cylinder block 2.

The valve plate 9 has a suction hole (not shown) which connects the cylinder bore 3 and the suction chamber 7, and the cylinder bore 3
And a discharge hole 12 communicating with the discharge chamber 8.

On the cylinder block 2 side of the valve plate 9, there is provided a metallic suction valve plate 13 having a reed valve (not shown) for opening and closing the suction hole, while the valve plate 9 is provided.
On the rear housing 6 side, a metal discharge valve plate 14 having a reed valve (not shown) that opens and closes the discharge hole 12, and a retainer 15 that holds the discharge valve plate 14 and restricts the open end of the reed valve. And are provided. The valve plate 9, the discharge valve plate 14, and the retainer 15 are fixedly fastened and integrated by a rivet R. And, between the valve plate 9 and the rear housing 6,
The gasket 16 is interposed to maintain the airtightness of the suction chamber 7 and the discharge chamber 8. Further, an O-ring is provided on the peripheral surface of the valve plate 9 to prevent the refrigerant from leaking to the outside of the compressor 1.

A shaft support hole 1 for rotatably supporting the drive shaft 10 through bearings 17, 37 and 18 is provided at the center of the cylinder block 2 and the front housing 4.
9 and 20 are provided.

In the crank chamber 5, a drive plate 21 fixed to the drive shaft 10 and a journal 24 swingably connected by a pin 23 to a sleeve 22 slidably fitted on the drive shaft 10, Boss portion 2 of the journal 24
5 is provided.

The drive plate 21 and the journal 24 have their hinge arms 21h and 24h formed in arc-shaped elongated holes 27.
Is connected via a pin 28 to restrict the swing of the swash plate 26. The piston 29 housed in each cylinder bore 3 is connected to the swash plate 26 via a pair of shoes 30 sandwiching the swash plate 26, and reciprocates with the rotational movement of the drive shaft 10 as a driving force. The basic function of the compressor 1 is that the reciprocating motion of the piston 29 compresses the refrigerant sucked into the suction chamber 7 → the suction hole of the valve plate 9 → the cylinder bore 3, and the cylinder bore 3 → the discharge hole 12 of the valve plate 9.
→ It discharges with the discharge chamber 8.

In order to make the discharge capacity variable, a bleed passage 31 (indicated by an arrow in FIG. 1) that constantly connects the crank chamber 5 and the suction chamber 7, and a supply passage that connects the crank chamber 5 and the discharge chamber 8 to each other. An air passage 32 (shown by an arrow in FIG. 1) and the air supply passage 32
A pressure control mechanism including a pressure control means 33 for opening and closing is provided. The bleed passage 31 is provided in the crank chamber 5
The refrigerant gas in the crank chamber 5 is returned to the suction chamber 7 according to the refrigerant gas pressure therein. The air supply passage 32
Is controlled by controlling the amount of the refrigerant gas that is opened and closed by the pressure control means 33 and flows from the discharge chamber 8 toward the crank chamber 5, thereby adjusting the pressure of the crank chamber 5 and changing the inclination angle of the swash plate 26. The discharge capacity of the compressor 1 is changed by changing the stroke. More specifically, the pressure control unit 33 changes the discharge amount of the compressor 1 according to the suction pressure of the refrigerant that returns to the compressor 1 to avoid freezing of the evaporator at the time of low load, and returns to the compressor 1. The air supply passage 32 is controlled to be opened and closed so that the suction pressure of the refrigerant to be kept constant.

Here, the extraction passage 31 has an extraction hole 10s provided in the drive shaft 10, a shaft support hole 19 provided in the cylinder block 2, an extraction hole 9s provided in the valve plate 9, and these shafts. The support hole 19 and the bleed hole 9s communicate with each other, and the bleed groove 2s provided on the rear end surface of the cylinder block 2 (see FIG. 3). In addition,
The bleed groove 2s in this example is provided in the bleed passage 31 in the middle of the bleed passage 31.
A fixed throttle portion (orifice) for narrowing the passage cross-sectional area of No. 1 is configured.

The bleed hole 10s provided in the drive shaft 10 forms an axial passage 35 provided along the axis of the drive shaft 10 from the rear end 10b of the drive shaft 10 toward the front end 10a. And a radial passage 36 that communicates with the axial passage 35 and opens directly to the crank chamber 5 to form an “inlet portion of the extraction passage 31”. In this example, the radial passage 36 forming the “inlet” of the extraction passage 31 is
Since it is formed outside the moving range of the sleeve 22, it is always open to the crank chamber 5.

According to the compressor 1 of the present embodiment having the above-described structure, the extraction passage 31 that constantly connects the crank chamber 5 and the suction chamber 7 is provided in the drive shaft 10, and the inlet portion of the extraction passage 31 is provided. Since the radial passage 36 constituting the above is directly exposed to the crank chamber 5, first, as shown in FIG. 2A, first, the mist-like oil that flows from the crank chamber 5 into the extraction passage 31 together with the refrigerant gas is removed. , Is collided with and captured by the inner peripheral surface of the radial passage 36 by the rotational movement of the drive shaft 10. That is, the radial passage 36 forming the inlet of the extraction passage 31.
The oil is separated (gas-liquid separation). Next, the oil adhering to the radial passage 36 is, as shown in FIG.
It is pushed back to the inlet terminal of and is discharged to the crank chamber 5 as it is.

Therefore, although the structure is simple, the oil is less likely to flow into the suction chamber 7 through the extraction passage 31, and the amount of oil flowing out from the extraction passage 31 can be reduced. Moreover, the oil scattered from the inlet end of the radial passage 36 into the crank chamber 5 automatically causes the crank chamber 5 to
Oil can be supplied to the sliding parts inside.

Here, Japanese Patent Laid-Open No. 58-158382 discloses a compressor in which a drive shaft is provided with a bleed hole formed of an axial passage and a radial passage. Is expected to have a centrifugal action due to the axial passage.
However, in this example, in the first place, the radial passage is closed by the sleeve to form the gap between the sleeve and the drive shaft as the inlet portion of the extraction passage, and the oil is provided between the sleeve and the drive shaft along the flow of the gas flow. Since it is a structure that tries to supply
The oil once entering between the sleeve and the drive shaft is difficult to be discharged, and is eventually taken into the suction chamber under the influence of the gas flow.

On the contrary, in this embodiment, since the radial passage 36 forming the inlet of the extraction passage 31 is directly opened to the crank chamber 5, the oil is generated by the centrifugal force of the drive shaft 10 as described above. Is pushed back to the inlet end of the radial passage 36 and is discharged to the crank chamber 5 as it is, so that the centrifugal separation effect can be utilized without waste, and the oil outflow amount from the extraction passage 31 can be reduced with a simple configuration. Moreover, the oil scattered from the inlet end of the radial passage 36 into the crank chamber 5 can automatically supply oil to the sliding parts in the crank chamber 5.

In this embodiment, since the radial passage 36 constituting the inlet of the extraction passage 31 is provided outside the moving range of the sleeve 22 due to the change in the discharge capacity, the radial passage 3
There is no concern that 6 will be blocked.

Actually, the effect of suppressing the lubricating oil outflow after the operating time of 0.5 hours of the compressor 1 of this embodiment was examined, and as shown in FIG. In comparison, the amount of residual oil in the crankcase 5 is increasing across the board.
Here, looking at the difference in the amount of oil remaining oil depending on the number of revolutions, it can be seen that the oil outflow suppression effect increases as the number of revolutions increases. This is because the centrifugal action of the radial passage 36 according to the present invention increases as the rotational speed of the drive shaft 10 increases. Also, looking at the difference in the amount of residual oil in oil depending on the outside air temperature, it can be seen that the higher the outside air temperature, the higher the oil outflow suppression effect. This is because when the outside air temperature is high, the heat load causes a large-capacity operation, and the blow-by gas amount increases accordingly. Therefore, the refrigerant gas amount returning from the crank chamber 5 to the suction chamber 7 through the extraction passage 31 increases. ing.

When the actual vehicle cooling power test of the refrigeration cycle using the compressor 1 having the oil outflow suppressing effect as described above is conducted, the COP value (= cooling performance [W] /
The power [W]) was improved by 9% under the condition of cool down for 3 minutes and improved by 12% under the condition of idling for 20 minutes, as compared with the conventional example. Further, the vent outlet temperature at this time was 1.8 ° C. lower under the cool down 3 minutes condition and 1.5 ° C. lower than the idling 20 minutes condition as shown in FIG. In addition, the actual vehicle cold power test is a cooling power test of the refrigeration cycle specified by our company, and the cool down operation in which the actual vehicle is operated at 40 [km / h] for 30 minutes and then at 100 [km / h] for 20 minutes After that, it means a cold power test under the condition of operating for 20 minutes in idling operation.

As described above, in the refrigeration cycle using the compressor 1 of the present embodiment, as the oil outflow amount from the compressor 1 is reduced as described above, the heat exchanger (condenser and evaporator) of the refrigeration cycle is connected to the heat exchanger. The oil inflow of
That is, it can be seen that the cooling performance of the refrigeration cycle is improved by reducing the amount of oil adhering to the thin tubes of the heat exchanger.
The conventional example shown in FIGS. 4 to 6 is a compressor in which the bolt through hole of the cylinder block 2 is used as an extraction passage.

As described above, according to the first embodiment, the extraction passage 31 is provided in the drive shaft 10 and the inlet portion 36 of the extraction passage 31 which directly faces the crank chamber 5 is set in the radial direction of the drive shaft 10. The oil outflow amount from the extraction passage 31 can be reduced with a simple configuration. Moreover, the oil scattered from the inlet end of the radial passage 36 into the crank chamber 5 can automatically supply oil to the sliding parts in the crank chamber 5.

Second Embodiment: FIG. 11 shows a compressor according to a second embodiment of the present invention. The same components as those of the above-described first embodiment are designated by the same reference numerals, and the description of the components and their effects will be omitted.

The compressor of the second embodiment differs from that of the first embodiment in that a seal member is provided. That is, in the second embodiment, the lip seal 41 as the “seal member” is attached to the drive shaft 10, and the lip seal 41
The gap between the inner peripheral surface of the shaft support hole 19 and the outer peripheral surface of the drive shaft 10 is sealed by the above.

According to the compressor of the second embodiment, the oil outflow amount can be further reduced by the sealing action of the lip seal 41. That is, the refrigerant gas in the crank chamber 5 is discharged from the extraction hole 10 as shown by the phantom line in FIG.
Bypassing s (35, 36), bearings 17, 3
7 and the inner peripheral surface of the shaft support hole 19 and the drive shaft 1
There is a possibility that the lip seal 41 gradually leaks from between 0 and the outer peripheral surface toward the downstream side of the bleed passage 31.
Thus, by preventing such bypass of the refrigerant gas, the oil outflow amount can be further reduced.

A lip seal 41 is provided closer to the rear housing 6 than the thrust bearing 37 and the radial bearing 17 (that is, downstream of the extraction passage 31). For this reason, the oil stored in the crank chamber 5 is not supported by the bearings 17, 3 due to a capillary phenomenon or the like.
7 is supplied.

A more preferred embodiment will be described below.
In the following embodiments, the same components as those in the first and second embodiments will be designated by the same reference numerals, and the description of the components and their effects will be omitted.

Third Embodiment: FIG. 12 shows a compressor according to a third embodiment of the present invention.

The compressor of the third embodiment is different from that of the second embodiment in that an oil supply passage 42 is provided.
That is, the oil passage 42 that opens from the axial passage 35 toward the bearing 17 communicates with the axial passage 35.

Therefore, in the compressor of the third embodiment, the oil that flows into the axial passage 35 and adheres to the inner peripheral surface of the axial passage 35 due to the centrifugal force is used as a sliding component. Can be supplied to the bearing 17.
Therefore, the durability of the bearing is improved.

In addition, in this embodiment, since the oil supply passage 42 is open to the crank chamber 5 side of the lip seal 41, the oil discharged from the oil supply passage 42 is separated from the lip seal 41 by the crank. It will exist in the area on the chamber 5 side. That is, the oil that once flows into the axial passage 35 is again discharged to the crank chamber 5 side region, so that the oil outflow amount can be further reduced.

Fourth Embodiment: FIG. 13 shows a compressor according to a fourth embodiment of the present invention.

The compressor of the fourth embodiment differs from that of the third embodiment in that a groove 43 is added to the axial passage 35. That is, in this embodiment, on the inner peripheral surface of the axial passage 35,
A linear groove 43 extending from the rear end of the drive shaft 10 toward the front end is provided.

According to the compressor of the fourth embodiment, since the groove 43 is provided on the inner peripheral surface of the axial passage 35, the oil flowing on the inner peripheral surface of the axial passage 35 is Most are captured in the groove 43. The oil captured in the groove 43 is less likely to be affected by the dynamic pressure of the refrigerant gas flowing in the axial passage 35, so that the downstream side X (the suction chamber 7
It is hard to be carried away to the side). Therefore, the oil outflow amount is further reduced. In addition, in the fourth embodiment, the inlet of the oil supply passage 42 is provided in the groove 43, which also has an advantage that the amount of oil discharged from the oil supply passage 42 is increased as compared with the third embodiment.

Fifth Embodiment: FIG. 14 shows a compressor according to the fifth embodiment of the present invention.

The compressor of the fifth embodiment differs from the compressor of the fourth embodiment in that the groove is a spiral groove 44. In addition,
Also in the fifth embodiment, the groove 4 is formed similarly to the fourth embodiment.
4 is provided with an inlet of the oil supply passage 42.

According to the compressor of the fifth embodiment, the groove 4
Since 4 is a spiral groove, in addition to the effects of the fourth embodiment, there are further preferable points. That is, since the groove 44 intersects the axial direction (the refrigerant gas flowing direction X), the oil trapped in the groove 44 is further less affected by the dynamic pressure of the refrigerant gas, and is less likely to be carried away to the downstream side X. Become. In other words, the spiral groove 44 is in the axial direction of the oil that can flow on the inner peripheral surface of the axial passage 35 (the flow direction X of the refrigerant gas).
Acts as a "resistor" that prevents flow to

Further, it is expected that the spiral groove 44 is used to push back the oil to the upstream radial passage 36 by utilizing the rotation of the drive shaft 10. The spiral groove 44 is formed as a screw groove formed by tapping from the rear end opening 46 of the drive shaft 10, for example.

Sixth Embodiment: FIG. 15 shows a compressor according to a sixth embodiment of the present invention.

The compressor of the sixth embodiment has a "resistor section".
Is formed as the stepped surface 48, which is different from the fifth embodiment in which the “resistive portion” is formed as the spiral groove 44. In this embodiment, by inserting the bush 47 from the rear end opening 46 of the axial passage 35 and fitting the bush 47 into the axial passage 35, the front end surface 48 of the bush 47 is moved in the axial direction (refrigerant). The annular step surface 48 is orthogonal to the gas flow direction X). That is, the step surface 4 as the "resistor portion"
8 impedes the flow of oil that can flow on the inner peripheral surface of the axial passage 35 in the axial direction (downstream side X of the refrigerant gas). As a result, the same function and effect as those of the fifth embodiment are obtained.

As described above in the first to sixth embodiments, according to the present invention, the extraction passage is provided in the drive shaft, and the inlet portion of the extraction passage that directly faces the crank chamber is set in the radial direction of the drive shaft. As a result, the oil outflow amount from the extraction passage can be reduced with a simple configuration. Moreover, it is possible to supply oil to the sliding parts in the crank chamber by the mist-like oil scattered from the inlet end of the radial passage into the crank chamber.

The present invention also includes modifications as the radial passage 36 as shown in FIGS. That is, in the present invention, a plurality of radial passages 36 forming the inlet of the extraction passage 31 may be provided, and as shown in FIG. 7, along the axial direction XY of the drive shaft 10. A plurality of drive shafts may be provided, or as shown in FIG.
There may be a plurality of those provided in the circumferential direction of 0 (for example, those formed through the entire width in the diametrical direction or those provided radially in the circumferential direction). Thus, the plurality of radial passages 3
In the case of being composed of 6, 36, ..., Since the amount of the refrigerant gas flowing into one radial passage 36 is reduced, the influence of the gas flow in each radial passage 36 is less likely to occur. There is an advantage that the centrifugal separation effect can be effectively exhibited.

Further, in the above embodiment, the sleeve 22
Although the radial passages 36 are formed outside the moving range of the sleeve 22, if the radial passages 36 have to be formed within the moving range of the sleeve 22, as shown in FIG.
The plurality of radial passages 36, 36 may be provided at intervals of the axial length d of 2 or more to open at least one radial passage 36 directly to the crank chamber 5.

Further, in the present invention, if the radial passage 36 extends in the radial direction from the inlet end of the radial passage 35 toward the axial passage 35 so that the centrifugal separation action is exerted, the axial passage is formed. 35 may be eccentric from the axis of the drive shaft 10, or the radial passage 36 may be inclined as shown in FIG. Here, although the radial passage 36 has the open position restriction as described above, the inlet end of the radial passage 36 is a sliding portion (for example, a sliding portion between a shoe pocket and a shoe, a shoe as shown in FIG. 10). And a swash plate), there is an advantage that oil can be more positively supplied to the sliding portion by the oil scattering utilizing the centrifugal force.

Further, although the swash type variable capacity compressor 1 is shown in the above-mentioned embodiment, the present invention can be applied to other variable capacity compressors such as a wobble type, and of course, a variable capacity compressor. Not limited to this, it can be applied to a fixed compressor.

[Brief description of drawings]

FIG. 1 is an overall view of a compressor according to a first embodiment of the present invention.

FIG. 2 is an enlarged view showing an inlet side of an extraction passage of the compressor, and FIGS. 2A and 2B are views showing an operation of oil separation by an inlet portion of the extraction passage.

FIG. 3 is an enlarged cross-sectional view of an outlet side of an extraction passage of the compressor.

FIG. 4 is a comparison diagram with a conventional example showing the lubricating oil outflow suppression effect of the compressor.

FIG. 5 is a diagram comparing the cooling performance of the compressor with a COP value in comparison with a conventional example.

FIG. 6 is a view comparing the cooling performance of the compressor with a vent outlet temperature in comparison with a conventional example.

FIG. 7 is a diagram showing a modification of the radial passage of the compressor.

FIG. 8 is a diagram showing a modification of the radial passage of the compressor.

FIG. 9 is a diagram showing a modification of the radial passage of the compressor.

FIG. 10 is a diagram showing a modification of the radial passage of the compressor.

FIG. 11 is a sectional view of essential parts of a compressor according to a second embodiment of the present invention.

FIG. 12 is a cross-sectional view of essential parts of a compressor according to a third embodiment of the present invention.

FIG. 13 is a sectional view of essential parts of a compressor according to a fourth embodiment of the present invention.

FIG. 14 is a sectional view of essential parts of a compressor according to a fifth embodiment of the present invention.

FIG. 15 is a sectional view of essential parts of a compressor according to a sixth embodiment of the present invention.

[Explanation of symbols]

1 compressor 2 cylinder block 3 cylinder bore 4 Front housing 5 crank chambers 6 rear housing 7 Inhalation chamber 8 discharge chamber 10 drive shaft 10s bleed hole 29 pistons 31 Extraction passage 35 Axial passage 36 radial passage (entrance of bleed passage) 37 Thrust bearing (bearing) 41 Lip seal (seal member) 42 Oil supply passage 43 groove 44 spiral groove (resistor part) 48 annular step surface (resistor part)

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Hiroyuki Makishima             Carso 5-24-15 Minamidai, Nakano-ku, Tokyo             Nick Kansei Co., Ltd. (72) Inventor Hiroshi Kageyama             Carso 5-24-15 Minamidai, Nakano-ku, Tokyo             Nick Kansei Co., Ltd. (72) Inventor Susumu Hinata             Carso 5-24-15 Minamidai, Nakano-ku, Tokyo             Nick Kansei Co., Ltd. F-term (reference) 3H003 AA03 AB06 AC03 BC01 BD09                       BH03                 3H076 AA06 BB15 BB17 CC20 CC36                       CC68

Claims (7)

[Claims] 1. A front end face of a cylinder block (2) having a cylinder bore (3) for accommodating a piston (29),
Crank chamber (5) by joining the front housing (4)
And a rear housing (6) is joined to the rear end surface of the cylinder block (2) to form a suction chamber (7) and a discharge chamber (8), and the shaft is supported in the crank chamber (5). The piston (2
In the compressor that reciprocates 9), a bleed passage (31) that constantly connects the crank chamber (5) and the suction chamber (7) is provided in the drive shaft (10), and the bleed passage (31) is provided. The inlet portion (36) of (1) is set in the radial direction of the drive shaft (10) and directly faces the crank chamber (5). 2. The compressor according to claim 1, wherein a bearing (1) is provided on the cylinder block (2).
A seal member (41) that seals a gap between the drive shaft (10) and a shaft support hole (19) that pivotally supports the drive shaft (10) via the drive shaft (7, 37). A compressor characterized by being attached to (10). 3. The compressor according to claim 2, wherein the seal member (41) is attached to the bearing (17, 3).
A compressor which is arranged closer to the rear housing (6) than to 7). 4. The compressor according to claim 3, wherein a portion (10s) formed in the drive shaft (10) in the extraction passage (31) is along an axial direction of the drive shaft (10). The axial passage (35) and the radial passage (36) communicating with the axial passage (35) and directly facing the crank chamber (5). (35) is connected to the bearing (1
A compressor characterized by being provided with an oil supply passage (42) opening toward 7, 37). 5. The compressor according to claim 1, wherein a portion (10s) formed in the drive shaft (10) in the extraction passage (31) is in an axial direction of the drive shaft (10). An axial passage (35) formed along the axial passage (35), and a radial passage (36) communicating with the axial passage (35) and directly facing the crank chamber (5). The directional passage (35) is provided with resistance portions (44, 48) that prevent the oil that can flow on the inner peripheral surface of the axial passage (35) from flowing in the axial direction (X). Compressor to do. 6. The compressor according to claim 1, wherein a portion (10s) formed in the drive shaft (10) of the extraction passage (31) is in an axial direction of the drive shaft (10). An axial passage (35) formed along the axial passage (35), and a radial passage (36) communicating with the axial passage (35) and directly facing the crank chamber (5). Grooves (43, 44) are formed on the inner peripheral surface of the directional passage (35).
A compressor provided with. 7. The compressor according to claim 6, wherein the groove (44) is a spiral groove (44) formed on an inner peripheral surface of the axial passage (35). Machine.